Rotating-piston pump



A. BULUTAY Aug. 1, 1967 ROTATING-P I STON PUMP 4 Sheets-Sheet 1 Filed NOV. 28, 1966 INVENTOR ATTILA BULUTAY AGENT Aug. 1, 1967 A. BULUTAY ROTATING-PISTON PUMP 4 Sheets-Sheet Filed Nov. 287 1966 m OE INVENTOR ATTILA BULUTAY g- 1, 1967 A. BUL UTAY 3,333,546

ROTATING-PISTON PUMP Filed Nov. 28, 1966 4 Sheets-Sheet 5 I'NVENTOR ATTILA BULUTAY BY I @59 2;

AGENT 1967 A. BULUTAY 3,333,546

ROTATING-PISTON PUMP Filed Nov. 28, 1966 4 Sheets-Sheet 4 Mb Fm. 3

EN ATTI BU AY AGENT United States Patent 3,333,546 ROTATING-PISTON PUMP Attila Bulutay, Sokak 7/2, Akay, Ankara, Turkey Filed Nov. 28, 1966, Ser. No. 597,356 Claims priority, application Turkey, Nov. 26, 1965, 39,676/12,420 (registered under No. 13,199) 10 Claims. (Cl. 103-429) ABSTRACT OF THE DISCLOSURE Rotary-motion, forced-action pump with two coaxial shafts having respective piston members associated therewith and performing advancing and lagging movements relative to one another. As a result of this periodic action, the volumes between the adjacent pairs of piston members expand and contract, thus providing the suction and discharge (intake and ejection) effects of the pump.

Various types of pumps are known which use dilferent principles for their operation. It has been determined some time ago that any oscillatory or irregular motion, such as that of reciprocating pistons, produces vibrations and subjects the pump to undue wear. Thus, preference has been given to rotary-action pumps, among which are screw types, centripetal, centrifugal, and other systems.

The present invention has as one of its major objects to dispense with the drawbacks and inherent disadvantages of hitherto used pump types. A rotary-motion, forced-action pump is provided which combines smooth operation with economical output and reliable performance.

It is another important object of the invention to provide such a pump which allows a wide range of adjustability, for controlling the suction and delivery phases, the output capacity, and/or the ejection pressure of the inventive pump, even independently from each other.

It is yet another object of the invention to dispense entirely with valves which are usually the source of disturbances in hitherto used types of pumps.

According to one of the important structural features of the inventive rotating-piston pump, there are provided two coaxial shafts, preferably one hollow and surrounding the other, which are driven by respective universaljoint systems. The latter provides periodic advancing and lagging movements in the shafts, and the piston members associated therewith, while they rotate in the same direction but with different and changing peripheral velocities.

According to the invention, consecutive piston members within a common cylinder space define compression spaces or volumes which are periodically expanded and contracted during the rotation of the shafts with the piston members. Preferably, a phase difference of 90 is provided between the movements of the two shafts.

Another feature of the invention relates to the provision of a liner inside the cylinder body, preferably pressfitted thereinto, the liner having passages which substantially correspond to the width of ,the input and output passages, and also to the compression volumes between the consecutive piston members. In a preferred, exemplary embodiment, this arrangement results in substantially identical-pairs of operational phases, namely A suction and C pumping, as well as B suction with pumping and D pumping with suction. From these, A and C are much shorter than B and D. These phases repeat themselves twice during each revolution of the driving shaft.

In the inventive pump, the shaft velocities are reduced twice and increased twice during one complete revolution of the two coaxial shafts. The resulting suction and compression allows the sucked-in water or other fluids to be ejected for delivery to the required manometric height.

Another feature of the invention relates to that the driving universal-joint systems are applied in a manner to present a 90 phase difference. Thus the volumetric suction rate, and consequently the output capacity are increased to a maximum. The maximum slow-down in the velocity of the one shaft, and the maximum speeding-up of the velocity of the other, are synchronized and this is performed in a periodical manner, as has been mentioned before.

A further feature relates to the adjustability of the volumetric suction rate and consequently the output capacity, by simply changing the specific angle between the axis of the coaxial shafts, on the one hand, and the axis of the driving shaft, on the other hand.

Yet another feature relates to that different suction ratios may be obtained by the facility of making the rotating pistons with larger or smaller volumes therebetween, which thus vary the overall volume of the pistons, occupying the total cylinder space.

The output capacity of the inventive pump can be brought to any desired rating by changing the phase difference of the universal-joint systems of the two shafts to any desired degree.

Another feature of the invention relates to that the pairs of suction and discharge sections in the cylinder space are kept unchanged during operation, without any relocation thereof. The channels leading to the afore-mentioned sections make for uninterrupted and continuous suction and discharge, without the necessity for valves and/or flaps.

Yet a further feature of the pump relates to the facility of operating the same even in reverse direction. In this mode of operation, the suction sections become ejection sections, and vice versa. Water is then withdrawn through the outlet channels, and it is ejected through the intake channels.

The various objects, features and attendant advantages of the present invention will become more apparent from the following description of a preferred exemplary embodiment of the rotating-piston pump according to the invention, when considered in conjunction with the accompanying drawings, wherein FIG. 1 is a top view of therottating-piston pump ac: cording to the invention;

FIGS. 20 and 2b are partial vertical axial cross-sectional and side-elevational views of the pump shown in FIG. 1, taken along line 2a, 2b of FIG. 3, wherein FIG. 2a illustrates two universal-joint systems for providing a periodical phase difference between the velocities of the two pump shafts, while FIG. 2b illustrates the pump 3, for explanatory purposes.

The inventive rotating-piston pump will now be described with reference to the top viewof FIG. 1 and the partial views of FIGS. 2a and 2b, the two together showing the pump on a somewhat enlarged scale so as to illustrate all important details. FIG. 3 and the detail views of-FIGS. 4a, 4b give cross-sectional details of '3 the rotating pistons and the operative spaces therebetween.

A bracket pad or plate 31 and a supporting angle bar 31a attached thereto serve as a chassis for the pump which is secured thereto by way of nuts 47 and bolts 49, with spring washers 46, 48 being preferably interposed therebetween.

The pump is driven by an input shaft 1 forming part or being operatively connected with a suitable prime mover. Within the pump, there are two driven shafts, namely an inner shaft 16 and a hollow shaft 17 surrounding the former. Before the actual pump components'can be dealt with, the two universal-joint systems will be described, as shown in FIGS. 1 and 2a, which are interposed between the driving or input shaft 1, on the one hand, and the driven shafts 16, 17, on the other, so as to provide a periodical phase difference between the velocities of these shafts, as will be fully explained hereunder.

Shaft 1 has connected thereto separate but coaxial and synchronously rotating yokes 32, 33, substantially perpendicular with respect to each other, to obtain 90 phase difference between said yokes, one for each universal-joint system. Following up first the yoke 32, which cooperates in driving the hollow shaft 17 with a periodically changing velocity, it is linked to conjugated ring members 4a, 4b by the intermediary of needle bearings 6 and lock rings 5 (see FIG. 2a). The members 4a, 4b are interconnected by means of bolts and nuts 2.

In the position shown in FIGS. 1 and 2a, yoke 32 is substantially in the horizontal plane and ring members 4a, 4b are in a plane perpendicular to the yoke 32 and to the axis of shaft 1. At respective angles of A (shown in FIG. 5) and 180 minus A, a second yoke 38 is journaled to the ring members 4a, 4b, similarly by the intermediary of bearings 6 and lock rings 5. The illustrated, preferred embodiment is made for A=30. The

'yoke 38 is perpendicular to the hollow shaft 17. As

shown in the drawings, the two pairs of bearings cooperating with the ring members are disposed diametrally, and

at right angles with respect to the other pair, for the driving and the driven yokes 32, 38, respectively.

An oil seal 3 is shown between the bearings 6 and the limbs of yoke 38, and similar seals may of course be.

provided for the other junctions of this and of the other universal-joint system. By way of a key 9, the yoke 38 is axially connected for driving the hollow shaft 17.

As to the other yoke 33, which cooperates in driving the shaft 16 inside the shaft 17 and independently therefrom, it is linked to conjugated ring members 35a,

35b similar to but smaller than the afore-mentioned members 4a, 4b. It will be seen from the drawings that yoke 32 and rings 4a, 4b are larger than their counterparts 33, 35a, 35b, respectively, so that the system of shaft 16 can freely rotate within that of shaft 17.

Here, again, there may be needle bearings and lock rings, as in the previously described universal-joint system. Bolts and nuts 34 serve for interconnecting the members 35a, 35b and they are of course the counterparts of bolts and nuts 2.

In the position shown in FIGS. 1 and 2a, yoke 33 is substantially in the vertical plane and ring members 35a, 35b are in a plane at respective angles of 30 and 150 Withrespect to the yoke '33 and to the axis of shaft 1. In a plane perpendicular to the axis of shaft 16 and to. the ring members 35a, 35b, a second yoke 37 is journaled to the latter, preferably also by the intermediary of bearings and lock rings. The bearing pairs are again disposed diametrally, at right angles for the driving and driven yokes 33, 37, respectively.

Oil seals 3 are again shown for this system. The yoke 37 is axially, directly (by way of a conventional key) or otherwise, connected to the end of shaft 16 for driving the same, independently from hollow shaft 17. An

oil seal 8 may be interposed between the enlarged end of shaft 16 and the outer end of hollow shaft 17 so as to prevent lubricants to escape from between the two shafts, in a conventional manner.

The pump proper includes right-hand and left-hand body portions 18, 18a, as viewed in FIGS. 1 and 2b. At the end where the shafts 16, 17 enter, there is a cap 11 having an oil seal 10 therein which surrounds the outer shaft 17. Between the cap 11 and the body porreferred to for most of the components to be described hereafter. Cylinder caps .20 straddle a cylinder body 21 which may be provided with heat-exchange fins, if required (not shown). Rotating piston members 23, having profiles as shown in FIG. 3, and similar members 58, are keyed to shafts 17 and 16, respectively, and members 23 have threaded bores therein for countersunk bolts 22 (see FIG. 2b). A cylinder liner 26 surrounds thepiston members 23 and 58. The afore-mentioned packings 19 are secured to cylinder caps 20 by way of packing bushes 28 and associated bolts 29.

At the end of the pump opposite the entrance of shafts 16, 17, body portion 18 is closed by a removable cap 30 allowing access to the end of shaft 16. At the opposite pump end, the cap 11 and the bearingcap 12 are held to the body portion 181: by. means of bolts 39, gaskets 40 and 41 being respectively interposed between the afore-mentioned elements, as shown in FIGS. 1 and 2b. Plugs 36 and 42 .are provided at strategic pointsof the pump casing for allowing lubricants to be introduced and drained, respectively. Between respective casing portions 18, 18a, the caps 20 and the cylinder body 21,

gaskets 44 and 45 are interposed; there is a similar. gasket 50 between the body portion 18 and the end cap 30 of the pump, as shown.

Numerals 51 identify attaching bolts similar to those shown at 39, and mentioned before; appropriate nuts 53 and optional spring washers 52 are also shown (e.g. in

FIG. 1) between the structural elements of the pump.

Similarly, bolts 54 and spring washers 55 are provided for holding the elements together (see FIGS. 1 and 2b). 7.

Again referrring to FIGS. 3, 4a and 4b, the piston members 58 associated with the shaft 16 are disposed at angularly offset locations with respect to the piston members 23 of shaft 17. The profiles of the members 58 are similar of pistons and shafts can be made as a single unit.

Referring now to FIGS. 1, 2b and 3 only, there are shown diametrally disposed inlets (see particularly FIG. 3) interconnected by a circumferential passage 76a which ends in a suction pipe 76. In another plane, axially spaced apart from the plane of the inlets, there are two diametrally disposed outlets which are also interconnected, by a circumferential passage 77a, terminating in an outlet pipe 77. The pipes 76, 77 have flanges 75 allowing attachment of the pump to other equipment. The passages 76a, 77 are equipped with air relief plugs 73. p

In FIG- 3, operative pumping spaces 65, 66, 67 and 68 are formed between successive pairs of piston'members 58 and 23 (then 23 and 58, and so forth). These spaces or volumes are aligned with respective channels 69, 70, 71

and 72, respectively connected with the afore-mentioned pairs of inlets and outlets which lead to the suction and outlet pipes 76, 77, respectively. The operation of the pump will be described as the description proceeds.

FIG. 5 is a schematic, explanatory illustration of the angular relationship between the shaft 1 and the shafts 16, 17; this view also shows the afore-mentioned specific angle A defined between the respective axes of these shafts, as will be explained somewhat later.

Coming now to the operation of the inventive rotatingpiston pump, it will be understood from the structural description that, during their rotation, the shafts 16, 17 perform advancing and lagging movements relative to one another, as a result of which the volumes 65 to 68 between the pairs of rotating pistons 58, 23 periodically expand and contract. This provides the suction and discharge (intake and ejection) effects of the pump. The diametrally opposite channels 69, 71 maintain constant suction while the other pair of channels 70, 72 discharges the pumped water or fluids. The expansion and contraction of the volumes 65 to 68 takes place twice during each revolution of the driving shaft 1.

When volumes 65, 67 contract, that is in the discharging position, volumes 66, 68 simultaneously expand, that is, they are at intake position. Subsequently, volumes 66, 68 become ready for discharging, and volumes 65, 67 for intake. This repeats itself periodically. The pumping or compression of the water or fluid discharged, performed by the device, is thus a rotary-motion, forced action.

Channels 69, 71 in cylinder 21 maintain constant suction, that is water or fluid is made to enter the cylinder. Simultaneously, channels 70, 72 maintain constant pressurized discharge from the cylinder. It should be noted that the cylinder liner 26 has passages therethrough which correspond in width to that of the respective channels 69 to 72; this width also corresponds to the profiled portion of the piston members 23, 58 which actually contacts the liner 26, as shown in FIG. 3. Thus, the piston members 23, 58 completely block the entrances to the channels when they coincide with the liner passages during their rotation.

Reference should be had at this point to the schematic, illustrative showing of the operational phases in the cylinder volumes, as shown in FIG. 6. For the sake of better understanding, the channels 69 to 72 and the respective passages in cylinder liner 26 have been shown in a single plane rather than offset by pairs, as in actual construction (see FIG. 3). Since both expansion and contraction or discharge take place twice during each revolution of the shafts 16, 17, there will be four distinct phases of operation during each half revolution, as identified in FIG. 6 by letters, to wit:

A-suction phase;

Bsuction phase, pumping section; C-pumping phase; and Dpumping phase, suction section.

The output capacity of the pump can be controlled by changing the rotational speed of the driving shaft 1, and/ or the volume of the cylinder 21, and/or the angle A" between the shaft 1 and the shafts 16, 17.

The manometric height of the delivered water or fluid can be proportionately increased by raising the power of the driving motor or prime mover acting on shaft 1, as far as admissible by the resistance of the materials used for the pump. It will be understood that the components of the pump, and mainly the cylinder 21, the caps 20 and the shafts 16, 17, may be made of friction and corrosionresistant materials.

It should be noted that there is no need to provide either valves or any other similar means for the intake or discharge channels of the inventive rotating-piston pump.

For purposes of illustration, driving shaft 1 can be as sumed to be rotated in the clockwise sense. However, it will be understood by those skilled in the art, that the shaft 1, and thus the pump, may be rotated in the reverse, counter-clockwise sense. Then channels 70, 72 will mainalternative mode.

It is also possible to maintain single-channel suction or discharge, or both, by separately interconnecting the two intake and/or discharge channels 69, 71, and 70, 72, respectively, by suitable conduits or other means, similar to the illustrated passages 76a and 77a.

.It will -be understood that no specific means have been described and illustrated for performing the various adjustments which have been described earlier, like the variation of the dimensions of the piston members; the changing of the specific angle between the various shafts; the changingof the volumes between the piston members; the variation in the phase angle or difference between the universal-joint systems of the two shafts; the adjustment of the volumetric suction rate and/ or the output capacity, etc. These will no doubt be self-explanatory expedients to those skilled in the art.

The foregoing disclosure relates only to a preferred,

.exemplary'embodiment of the inventive pump, which is ed between said driving shaft and said driven shafts,

for simultaneously rotating said driven shafts with a phase difference and with periodically recurring independent speeding-up and slowing-down phases in the velocities of each driven shaft; a casing body including a closed cylinder body, a cylinder liner fitted into said cylinder body and defining a compression chamber; a pair of diametrally disposed piston members operatively connected with each driven shaft, the two pairs being normally perpendicular with each other, and rotatable within said compression chamber with a predetermined phase advance and phase lag in each pair of piston members, upon rotation of said driven shafts; a pair of diametrally disposed inlet channels through said cylinder body and said liner, and a pair of outlet channels spaced apart from said inlet channels along the common axis of said driven shafts; the spaces between successive piston members, connected with different driven shafts, periodically expanding and contracting so as to provide suction for water and fluids through said inlet channels, and consecutively to provide compression for the water and fluids to deliver the same through said outlet channels; said liner having passages aligned with said inlet and said outlet channels and substantially corresponding in their diameters to those of said channels and to the active lengths of the outer sides of said piston members; whereby four distinct operational phases result during each half revolution of said driving shaft, namely a suction phase for the water and fluids, a suction phase with pumping, a pumping phase and a pumping phase with suction, the firstand third-named phases being much shorter than the secondand fourth-named phases, each pair of said phases having substantially the same length.

2. The pump as defined in claim 1, wherein said phase difference is substantially between the movements of said driven shafts.

3. The pump as defined in claim 2, wherein said universal-joint systems each include ring members to which said driving and said driven shafts are operatively linked by yokes, one of said yokes in each system being perpendicular with respect to the connected shaft while the other yoke defines angles of 30 and degrees with respect to the other connected shaft; the universal-joint systern of one driven shaft being larger than the other so as toaccommodate the latter within its ring members, with full freedom of rotation.

4. The pump as defined in claim 3, wherein said yokes in at least one of said universal-joint systems are disposed for pivotal Connection with said ring members at diametrally opposite points on the side of said driving shaft, and at similar diametrally opposite points at right angles to the afore-mentioned points on the side of said driven shaft.

5. The pump as defined in claim 1, wherein at least one pajrof said inlet and said outlet channels is interconnected for common passage of the water and fluids, and wherein at least one of said channels is provided with air relief means.

6. The pump as defined in claim 1, further comprising at least oneset of piston rings disposed on said piston members connected with at least one of said driven shafts, and spring means lodged in bores of the afore-mentioned piston members for biasing said piston rings toward said cylinder liner.

7. The pump as defined in claim 1, wherein said piston members have a butterfly shape which is wider on the inner side adjoining the respective driven shaft and narrower on the outer side where said piston members are in sliding contact with said cylinder liner.

8. The pump as defined in claim 1, further comprising bearing means in said casing body for said hollow shaft, bearing needlesbetween said driven shafts and accommodated in recesses of the surrounded driven shaft, and at least one oil seal associated with said driven shafts for preventing leakage of lubricant from said casing body.

9. The pump as defined in claim 8, wherein said hollow shaft is shorter than the other driven shaft, and oil seals are disposed between said driven shafts at both ends of said hollow shaft.

shafts, the size of said spaces between successive piston members, the volume of said compression chamber, the output capacity, the ejection pressure, the volumetric suction rate and the desired manometric height of the delivered water and fluids, and further comprising means for varying at least one of the afore-mentioned parameters.

References Cited UNITED STATES PATENTS 1,502,756 7/ 1924 Thompson 103129 2,072,482 3/1937 Myard 103129 2,148,282 2/ 1939 Stevens 103129 2,149,143 2/ 1939 Landenberger 103129 2,182,269 12/ 1939 Whritenour 123-11 2,503,894 4/ 1950 Wildhaber 103129 2,553,954 5/1951 Bancroft 230'144 2,642,807 6/ 1953 Linderman 12311 2,673,027 3/ 1954 Lipkau 230144 2,811,927 11/1957 Jansen 103129 3,061,180 10/ 1962 Dnrgin 230-144 3,139,871 7/ 1964 Larpent 123-11 FOREIGN PATENTS 976,094 10/ 1950 France. 465,211 5/ 1937 Great Britain.

DONLEY J. STOCKING, Primary Examiner.

W. J. GOODLIN, Assistant Examiner. 

1. A ROTATING-PISTON PUMP FOR WATER AND FLUIDS, COMPRISING A DRIVING SHAFT ROTATED BY AN EXTRANEOUS PRIMEMOVER AT A SUBSTANTIALLY UNIFORM SPEED; TWO DRIVEN SHAFTS, ONE OF THE BEING HOLLOW AND COAXIALLY SURROUNDING THE OTHER; TWO UNIVERSAL-JOINT SYSTEMS OPERATIVELY INTERCONNECTED BETWEEN SAID DRIVING SHAFT AND SAID DRIVEN SHAFTS, FOR SIMULTANEOUSLY ROTATING SAID DRIVEN SHAFTS WITH A PHASE DIFFERENCE AND WITH PERIODICALLY RECURRING INDEPENDENT SPEEDING-UP AND SLOWING-DOWN PHASES IN THE VELOCITIES OF EACH DRIVEN SHAFT; A CASING BODY INCLUDING A CLOSED CYLINDER BODY, A CYLINDER LINER FITTED INTO SAID CYLINDER BODY AND DEFINING A COMPRESSION CHAMBER; A PAIR OF DIAMETRALLY DISPOSED PISTON MEMBERS OPERATIVELY CONNECTED WITH EACH DRIVEN SHAFT, THE TWO PAIRS BEING NORMALLY PERPENDICULAR WITH EACH OTHER, AND ROTATABLE WITHIN SAID COMPRESSION CHAMBER WITH A PREDETERMINED PHASE ADVANCE AND PHASE LAG IN EACH PAIR OF PISTON MEMBERS, UPON ROTATION OF SAID DRIVEN SHAFTS; A PAIR OF DIAMETRALLY DISPOSED INLET CHANNELS THROUGH SAID CYLINDER BODY AND SAID LINER, AND A PAIR OF OUTLET CHANNELS SPACED APART FROM SAID INLET CHANNELS ALONG THE COMMON AXIS OF SAID DRIVEN SHAFTS; THE SPACES BETWEEN SUCCESSIVE PISTON MEMBERS, CONNECTED WITH DIFFERENT DRIVEN SHAFTS, PERIODICALLY EXPANDING AND CONTRACTING SO AS TO PROVIDE SUCTION FOR WATER AND FLUIDS THROUGH SAID INLET CHANNELS, AND CONSECUTIVELY TO PROVIDE COMPRESSION FOR THE WATER AND FLUIDS TO DELIVER THE SAME THROUGH SAID OUTLET CHANNELS; SAID LINEAR HAVING PASSAGES ALIGNED WITH SAID INLET AND SAID OUTLET CHANNELS AND SUBSTANTIALLY CORRESPONDING IN THEIR DIAMETERS TO THOSE OF SAID CHANNELS AND TO THE ACTIVE LENGTHS OF THE OUTER SIDES OF SAID PISTON MEMBERS; WHEREBY FOUR DISTINCT OPERATIONAL PHASES RESULT DURING EACH HALF REVOLUTION OF SAID DRIVING SHAFT, NAMELY A SUCTION PHASE FOR THE WATER AND FLUIDS, A SUCTION PHASE WITH PUMPING, A PUMPING PHASE AND A PUMPING PHASE WITH SUCTION, THE FIRST- AND THIRD-NAMED PHASES BEING MUCH SHORTER THAN THE SECOND- AND FOURTH-NAMED PHASES, EACH PAIR OF SAID PHASES HAVING SUBSTANTIALLY THE SAME LENGTH. 